Pick motion for looms



Feb. 9, 1960 Filed March 24, 1958 J. A; MORIN PICK MOTION FOR LOOMS 5 Sheets-Sheet 1 INVENTOR JOSEPH A. MORIN g flzwmz Feb. 9, 1960 J. A. MORIN PICK MOTION FOR LOOMS 3 Sheets-Sheet 2 Filed March 24, 1958 IHVENTOR I JOSEPH A. MORI N 6' I v f J. A. MORIN PICK MOTION FOR LOOMS Feb. 9, 1960 Filed March 24. 1958 3 Sheets-Sheet 3 mvsm'ow. JOSEPH A. MORIN ATTYS United States Patent PICK MOTION FOR LOOMS Joseph A. Morin, Gait, Ontario, Canada, assignor to Textile Development and Machinery Limited, Gait, Ontario, Canada Application March 24, 1958, Serial :No. 723,605

20 Claims. (Cl. 139-142) This invention relates to looms and more particularly to a side pick motion therefor embodying a new and improved method of operation.

Hitherto, the shuttle of virtually all looms has been operated by a vertically disposed picker stickpo'wered independently and having no positive operative connection to the lay motion. ()ne great disadvantage inherent .in the vertical pick motion is that the mechanism for operating the pick is mounted at a very low level and a number of the operating parts are situated underneath the loom between the side frames thereof. The independent lay motion embodies crank mechanisms which are also operated in the area between the side frames of the loom underneath the warp strands. In addition to inaccessibility and diliiculties of maintenance, the difficulty of keeping the space underneath the loom clean results in an unnecessary fire hazard which reflects in higher tire insurance premiums. Furthermore, due to the mechanism operating underneath the warp strands, splashing lubricant sometimes soils the warp strands, spoiling the material that is produced.

The speed at which a loom can operate satisfactorily generally depends upon the Width of the loom. The wider the loom, the fewer picks per minute that are possible. An enormous amount of research and experiment has been carried out in the past few years with a view to increasing the maximum number of picks per minute of which a loom of given width is capable.

Current types of looms possess several other sources of difficulty which bear on the quality of the fabric produced in any given instance. For example, the rate of wear on shuttles and picker sticks is generally higher than the rate of wear on other parts of the machine and renewal of a shuttle or picker stick necessitates the shutting down of the loom concerned, and restarting with a new shuttle or picker stick in which case the product produced will not be identical with that produced before the replacement.

It has moreover been found to be very important that the shuttle move in a true path without vibration, for, on the one hand, a vibrating shuttle tends to break the filaments in the warp andweft strands giving the cloth a rough or uneven texture, while on the other hand, an uneven shuttle movement tends to lay the weft in an uneven manner which also results in an inferior fabric. An uneven shuttle movement also tends to produce a frayed selvedge. I According to my invention, the above diificulties are removed or minimized and the maximum number of picks per minute possible is increased by about 15 to 20% by the use of a new side pick motion and method of operation as will he hereinafter described.

My invention contemplates the operation of a side pick motion in the following'manner:

The horizontal component of the lay movement, which is of the conventional type, is transmitted to horizontally reciprocable pick motion'carriages. These reciprocating carriages carry the picker sticks and picker stick actuat- .prising a carriage; securing means for said carriage designed to attach to the side frame of a loom and permit said carriage to reciprocate longitudinally of the loom; connecting rod means for transmitting the longitudinal component of the lay motion of the loom to said carriage; a picker stick longitudinally pivoted at one end on said carriage and designed operatively to co-operate with a pick of the loom; a power arm horizontally pivoted at a point intermediate the ends thereof on said carriage; connector link means in operative pivotal correction with said picker stick intermediate the ends thereof, one end of saidpower arm being pivotally connected to said connector link means; cam co-operating means carried by the other end of said power arm, said cam co-operating means being adapted to co-operate with a power cam moving in timed relation to the lay motion of the loom to operate the picker stick; and spring means in connection with said power arm for returning said picker stickto its initial position after operation thereof.

Preferably, according to my invention, the loom is driven by a drive shaft which extends across the loom and drives a countershaft. The motion of the lay is derived from the countershaft, while at either end of the drive shaft is mounted a cam wheel upon the face of which is mounted a suitablecam rise designed to actuate the picker actuating means. It will be appreciated that if one cam rise is at to the other and the drive ratio of the driveshaft to the countershaft is 1:2, the cam rise and picker stick actuating means on either side of the loom will converge alternately, and the lay will be carried forward in the interval between such convergence to one side of the loom, and such convergence on the other, that is to say-following each travel of the shuttle across the loom.

One embodiment of my invention is described specifically in conjunction with the accompanying drawings in which:

Figure 1 is a general diagrammatic plan view of a loom showing the general positioning of the apparatus of the invention in relation to the conventional compo nents of the loom.

Figure 2. is a side View of a loom illustrating the various parts diagrammatically in the same manner and for the same purpose as in Figure 1.

Figure 3 is a cross sectional view of a loo-m embodying the invention.

Figure 4 is a perspective view of the side pick motion mechanism showing the inter-relation of the various parts in detail. The mechanism shown in Figure 4 is a mechanism shown on the left hand side of Figure 3.

Figure 5 is a partly cut-away perspective view of the shuttle box of the loom illustrating the mounting of the pick itself and the co-operation between the pick and the picker stick.

Figure 6 is an enlarged cross section showing the I structure of. the-pick itself.

F atented Feb. 9, 1966 Figures 1 and 2, the conventional parts of the loom, which are here represented diagrammatically in dotted outline,

mounting of the mechanism which forms a part of the invention. The side pick motion assemblies 18, described in detail below, are positioned at either side of the loom outside the side frames 16 and behind the lay so that the ends 19 of the picker sticks, which are operated by the pick motion assemblies, project horizontally to co-operate with the picks which are situated within the shuttle boxes at either end of the lay 13.

The drive shaft 20 is mounted on suitable hearings in the side frames 16 and mounted at either end thereof are the cam wheels 20a. By means of the gear 21 and the pinion 22, power is transferred to the countershaft 23 and the usual heddle motion power take off is conveniently mounted on the drive shaft 20 and usually includes the eccentric cam 24. It should be noted at this point that the mounting of the side pick motion assembly in the position shown eliminates all moving parts underneath the loom and leaves the space within the supporting stand 17 completely free of working parts and readily accessible for cleaning purposes.

Referring now to Figure 4 which illustrates the side pick motion mechanism on the side of the loom to which power is supplied (that on the other side of the loom being identical except for the lack of power supply means), it will be seen that the drive shaft 20, carrying cam wheel 20a and the gear 21 is disposed horizontally and is driven by the pinion 25 which is connected to a source of power by means of the shaft 26, the clutch sheave 27 and the V-belt 28. The power source may suitably be an electric motor 29 of suitable horse power as partially shown on Figure 3. As previously mentioned, the pinion 22 is driven by the gear 21 and has exactly half the number of teeth that the latter has so that for every revolution of the gear 21, the pinion 22 will revolve twice. Mounted on the eccentric pivot 30, which is secured to the pinion 22, is the link 31 which is pivoted in the bracket 32 which is secured to the lay 13. The lay itself is mounted upon the lay pivot arms 14 which are pivoted at their lowerends 14a about the spindle 33. Thus it will be seen that as the gear 21 rotates through one revolution, the lay will be caused to rock backwards and forwards twice, pivoting about the spindle 33.

Intermediate the ends of the link 31, is the bushing 34 in which is pivotally socketed one end of the pump rod arm 35. The other end of the pump rod arm 35 is pivoted to the pivot pin .36 extending laterallytinwardly from the bushing 37 whichis mounted on the pick motion carriage 38. The bushing 37 is mounted on and slidable longitudinally with respect to the pump rod spindle 39 which is secured in the bushings 40 and 41 which are secured to the picker mechanism supporting bracket 42.

Thus it will be seen that as the link 31 causes the lay to rock,backwards and forwards, pivoting about the spindle 33,the horizontal. component ,of this movement of the lay will be imparted to the picker motion carriage 38 which will be caused to move back and forth along the pump rod 39 in accordance with the movement of the lay.

The picker motion carriage 38 is supported in a' substan tially horizontal position by virtue of the underside of the guide portion 43 thereof ridinglon the top of the cam wheel 20a on the cylindrical periphery 44 thereof; The guide portion 43 is right angular in cross section and embodies the vertical portion 45 which extends downwardly immediately to the loom side of the cam wheel 20a 7 4 v t anti-friction washers 47, is the picker stick 48. The picker motion carriage is also provided with a pivot pin 49 about which is pivoted the substantially Z shaped power arm 50, one end of which is provided with the cam roller 51 which is mounted adjustably in the slot 52.

The cam roller 51 is adapted operatively to engage the power cam 53 as it is revolved by the drive shaft 20. The

' other end of the power arm 50 is pivoted to the connector for a purpose which willbe ,de scribedlater. Pivoted on the pivot bolt 46 which is secured in a suitable boring on 54 which has a bifurcated portion 55 through which the picker stick passes. The bifurcated portion 55 terminates in a pivotal connection 56 to the power adjustment bracket 60.

From the detail view of the power adjustment bracket shown in Figure 7, it will be seen that the power adjustment bracket consists of an arm 60 with a bent portion including a pivot pin socket61 at one end thereof, and a bolt securing car 62 at the other end thereof. The power of the throw of the pick or stick may be adjusted by altering the position of the bolt 58 in the slot 59 since it will be seen that this willalter the moment of any force supplied through the connector 54 about the pivot point 46 of the picker stick 48. Also mounted in a suitable hole in the power adjustment bracket 60,. is the throw adjustment bolt 63 whichicarries adjustment nuts 64 and 65.

It will be seen that by varying the protrusion of the head of the bolt 63 through the arm 60, the angle at which the picker stick rests may be varied.

In order to ensure return of the picker stick and power arm to their initial. position after operation, the coil spring 66 is provided, secured at one end on the pivot,

wardly to connect to a further bearing support 70 which contains a bearing for the shaft 26. Theshaft 26 has the hand wheel 71 mounted thereon and also mounts the clutch sheave 27 and the clutch actuator 72 which is of conventional design and enables the working parts of the loom to be shut off withoutshutting down the electrrc motor 29. The hand wheel 71 is used to move the working parts of the loom by hand when setting various timing adjustments. It will be noted from Figure 3 moreover that the conventional heddle action take off: consisting of the eccentric cam means 24 and the sprocket. chain drive 24a are mounted on the drive shaft 20 at the driven end thereof, in which position they do not interfere with the operation of the other parts of the loom and are in a convenient position for adjustment and maintenance.

through the slot 72 in the shuttle box 73 and passes through theopening 74 in the pick 75. The pick is of conventional design. and is adapted to slide back and forth on the pick spindle 76 under the influence of the picker stick 48. The pick spindle 76 is supported at one end in the bracket 76a in the end of the shuttle box and at the other end in the spindle supporting block 76b which is secured to the shuttle boxby the bolt means 76c. The leather bumper 76d is mounted at the inner end of the pick spindle, to prevent damage to the picker and picker spindlesupporting block, and reduce vibration of thelatter which wouldbe aggravated were the pick to be carried into contact with the pick spindle supporting box at the end of each stroke. r

The pick 75 is composed of the usual vulcanized cotton fibre composition and embodies the usual conical recess, 77 for reception of the pointed end 78. of. the shuttle 79.

The pick spindle 76 isv mounted in the shuttle box. below the slot 80 in such a position that the cylindrical portion 81 of the pick, with the conical recess 77 therein, extends on the upper side of the slot 80 with the cylindrical portion 81 in co-axial relation to the shuttle 79. This co-axial relationship. of the cylindrical top portion of the pick to the shuttle is most important in any shuttle loom since it is only under such conditions that the shuttle can be made to follow an absolutely-true course across the lay.

The alternative form of power arm assembly shown in Figure 8 is merely a. simplification ofthe power arm arrangements shown in Figure 4 eliminating the power adjustment bracket and the fittings therefor as well as the pivotal connection of the picker stick to the pick motion carriage 38. In the simplified arrangement shown in Figure 8, the power arm 32 is of a slightly bent shape and pivots about the pivot 83 which is mounted on the picker motion carriage similarly to pivot 49 already described in connection with Figure 4. The cam.roller 84 is mounted in a slot 85 in one end of the power arm 82 and secured in adjusted position by the bolt means 86 which also secure in :rigid relation, the lower picker stick connector. bar 87. The latter is rigidly connected to the picker stick by the bolt means 88 passing through the slot 89 and asuitable holein the picker stick 48. The other end of the power arm-82 is secured to an upper connector bar 90 by the bolt means 91 which pass through a suitable hole in the upper connector bar 90 and the slot 92 in the power arm 82. The upper connector bar 90 is secured to the picker stick by the bolt means 93 passing through a suitable hole in both the upper connector bar 90' and the picker stick 48. Thus it willbe seen that by adjusting the position of the bolt 88 in the slot 89, the angular position of the picker stick may be varied, while adjusting 'the positions of the bolts 86 and 91 in the slots 85 and 92 respectively and the angular disposition of the lower and upper connector bars 87 and 90 respectively, will vary the power of the picker stick stroke. In this manner, the functions of the power adjustment bracket. 60 are carried out by means of a simplified construction.

The operation of the side pick motion above described is as follows:

Power supplied by the electric motor 29 is transmitted by the V-belt 28 to the clutch sheave 2'7 and through the shaft 26 to the pinion 25 as will beseen from Figures 3 and 4. The pinion 25 meshes with the gear 21 causing the latter to rotate. Rotation of the gear 21 in turn, causes the pinion 22 to counter-rotate and, since the drive ratio of the gear 21 to the pinion 22 is 1:2, each revolution of the gear 21 will cause two counter revolutionsof the pinion '22. As the pinion 22 rotates, it causes a back and. forth motion of the connecting rod. 31 which in turn causes a reciprocating motion of the lay 13:which is. thus caused to pivot back and forth about the pivot spindle 33 to take on the conventional motion peculiar to lays in shuttle looms. By. means of the pump rod arm 35, the pick motion carriage 38 is caused to slide back and forth along the pump rod spindle 39 audit will be seen that the motion imparted to thepick motion carriage will be the horizontal component of thevmotion imparted to'the lay 13 and that the lay and pick motion carriage will move back. and forth in synchronization; As the gear 21 rotates, the cam wheel. 20a also rotates, carrying with it the power cam 53 which is mounted in appropriate position so that as the: lay is returning from the operation of laying a weft strand, the cam 53 moves into contact with the cam roller 51. and the combination of the backward motion of the pick motion carriage 38 and the forward rotating motion of the .power. cam. 53 causes the cam roller 51 to be sharply thrust outwards in conformance with the working contour of the power cam 53. This causes the power armtopivot about the pivot 49 on the pick mo.- tion carriage, carrying with it the connector 54, causing the. picker stick sharply to be swung angularly about'the pivot-46.- The end 19 of the picker stick which ,passes through the opening 74 in the pick 75, carries thepick alongthe pick spindle 76, the conical recess 77 seats the pointed end 78 of the shuttle and imparts to the shuttle sufiicient velocity to carry it through the shed and into the shuttle box on the far side of the loom.

At the point when the cam roller 51- first meets the contour of the power cam 53, a terrific axial thrust isgenerated, tending to forcethe cam wheel 20:? alongthe gear shaft 20 towards the gear. 21. This tendency is minimized and a considerable amount of strain is relieved by the depending portion 45 of the guide portion 43 of the pick motion carriage, and instead of being urged along the shaft 20, the cam wheel 20a and power cam 53. arermerely squeezed between the portion 45 of the guide portion 43 and the cam roller 51. It should be mentioned at this point that by having the cam 53 and the cam roller 51 meet in a converging manner, a very positive quick pick action isv accomplished. Furthermore, this desirable pick motion is achieved with a minimum of 'vibrationsince at no time do any rapidly mov-' ing parts of the motion come to rest against any fixed parts of the loom. I

As. previously mentioned, the power cams 53 at opposite ends of the drive shaft 20 are at an angle of to each other. Thus, no sooner will the shuttle have made its trip through the shed to the opposite shuttle box than the lay will move forward to lay the new weft strand and commence its return, at which point the power cam 53 on the opposite side of the loom will be moving into contact with the cam roller 51 on that side of the loom and the same sequence of motion as is described in the preceding paragraph causes the shuttle to be returned through the shed to its starting point where it will arrive just as the lay is completing its return motion and where it will stay until the lay has completed its next forward motion and commences again to return. At this point the cam wheelZtla .will just be completing its first revolution.

The motion described gives a veryeven pick which has been found to nearly double the lifeof the shuttle and the picker sticks. Moreover, in giving an even pick to the shuttle, the shuttle is caused to travel a very evenpath with the result that thereis a considerably reduced breakage of the filamentsin both the warp and weft strands, so that a final product of smoother texture is produced, and a more uniform selvedge is formed.

It will be apparent moreover, that the adjustment of the side pick motion described is very simple, involving principally adjustment of the picker stickitself in the power adjustment bracket, and the adjustmentof the position of the cam roller 51 in the slot 52. Once these adjustments are made, the loom will run for a very long period of time without requiring further adjustments.

In order initiallyto adjust the side pick motion, the mechanism is operated manually, by turning the hand wheel 71 until the pivot 30 is at top dead centre positionand the cam roller 51 is then adjusted into contact with the contour of the power cam 53.

This ensures that earn roller 51 and the power cam 53 will meet when thecam roller 51 is midway along its return travel, at its point of. maximum velocity. At this point, the angular adjustment of the picker stick, which is controlled by the adjustment bolt 63, should be adjusted until theend 19' of the picker stick 48 extends through the slots 72 in the shuttle box at the outer end thereof. As far as the adjustment of the pivot 58 is concerned, it will be seen that the further; up the slot I 59 this bolt is adjusted; the smaller will be theangular movement of thepicker stick and.thus,:.therlower the .velocity imparted in the shuttle. Proper adjustment for power is a matter. of experience when operating at any given loom speed. In Figure 4, the power adjustment bracket is shown in adjustment for maximum power and hence, highest possible shuttle speed.

The simplicity of the adjustment of the side pick motion described, makes it possible for an untrained man to obtain a complete undeistanding of the mechanism in approximately one week, and enables a man to become competent to operate such a mechanism in a much short- "er time. This is a considerable advantage over previous pick motions where years of experience were sometimes necessary to obtain a complete understandingof the V mechanism.

As an indication of the increase in speed possible when using a pick motion of the invention it should be mentioned that it has been found, when using the simplified power arm assembly shown in Figure 8, an 84" loom can be operated at a speed of 122 picks per minute as against 102 picks per minute on conventional looms using thevertical pick motion. It has been found that a general increase of to in the operatingspeed of looms is possible when using the side pick motion of the invention on a 100m of any given width.

A most important feature of the invention is the fact that in order to convert a conventional loom with a vertical pick motion to a loom embodying the applicants invention, it is merely necessary to remove entirely the vertical pick mechanism and lay motion crankmecha' nism, mount the drive shaft and counter-shaft of the invention in suitable position on the side frames and then secure in'position by means of suitable brackets supported from the side frames of the loom, the pick motion assembly of the invention. Thus the conversion is a very simple matter, and complicated and time consuming fitting of parts in the actual loom factory is reduced to a minimum. I claim:

1 In a shuttle loom; a lay; means for imparting conventional reciprocating motion to said lay; a pick motion carriage; means for imparting the horizontal component of the lay motion to said pick motion carriage; cam means; fixedly mounted rotatable supporting shaft means for said cam means designed to rotate said cam means once for every twoforward movements of 'said lay in timed relationthereto; a picker'stick and actuating means therefor'rnounted on said pick motion carriage, said actuating means comprising cam roller means mountedin position operatively to converge into contact with said cam means once for every revolution thereof to' actuate said picker stick; and means for returning the picker stick and actuating means therefor to theoriginal position thereof after actuation thereof.

2. A shuttle loom, including components, as defined in claim 1 in which the picker stick and actuating means therefor comprise a power arm horizontally pivoted intermediate the ends thereof on said pick motion carriage, one end of said power arm having said cam roller means mounted thereon, the other end of said power arm being pivoted toconnector means operativelyconnecting to a point intermediate the ends of said picker stick, and wherein said picker stick is horizontally pivoted on said pick motion carriage, whereby said power arm is caused abruptly to rotate and cause actuation of said picker stick upon contact between said cam roller and said cam means.

3. A shuttle loom as defined in claim 2 comprising means for adjusting the position of said cam roller means said power arm comprises an adjustment slot in said 1 powenarm, and adjustable securing boltmeans'on said cam roller means.

5. 'A shuttle loom as defined in claim 2 comprising means for adjusting the powerof the throw ofthe'pick'.

. 6- A shuttle loom as defined in claim 5 in which said.

means for adjusting the power of the throw of the pick comprises a longitudinal slot in said picker stick, and bolt securingmeans designed to be adjustably secured therein, the po sitionof said boltsecuring means governing the leverage of said connector means about the pivot ofsaid pickerfstick. v

7.Ashuttle loom as defined inclaim 2 comprising apower adjustment bracket secured to said picker stick and "pivotally connecting to said connector means, said power adjustment bracket beingadjustable longitudinally of said picker "stick to alter the leverage of said connector means about the point of pivot of said picker stick.

8. A shuttle loo-m asdefined injclaim7 in which said power adjustment bracket comprises adjustment bolt means for adjusting the angular disposition of the picker "stick therein. i

9. A shuttle loom including componentsas defined in claim 1 in which the picker stick and actuating means there-for comprise a power arm horizontally pivoted intermediate the endsthereof on said pick motion carriage, one end of saidpower arm having said cam roller means mounted'thereon; lower connector bar means rigidly connec'ting saidend of said power arm to the end -of the picker stick and upper connector bar means rigidly connecting the otherflend of said power arm to a point intermediate the ends of said picker stick.

10; A shuttle loom as defined in claim 9 in which the cam roller means is mounted in adjustable relation to the end of said power arm.

11. A shuttle loom as defined in claim 9 in which at which at least one of said upper and lower connector bar means contains an adjustment slot designed to accommodate a securing bolt whereby the effective length of said connector =barmay be varied and in which the angular dispositions of said connector bars with relation to said picker stick and power arm are adjustable.

12. A shuttle loom as defined in claim 11 in which the lower connector .bar and the cam roller means are mounted on the end of the power arm on a common rods pivotally connecting tothe lay, in connection with isaid couter shaft for imparting said reciprocating motion to the lay, said drive shaft alsohaving said cammeans mounted thereon.

14. A shuttle loom, including components, as defined in claim 1 in which said pick motion carriage is slidablymounted on a spindle supported from the side frame.

of the loom, and in which the means' forimparting the horizontal component of the lay motion thereto comprisespump rod means connecting said pick motion carriage to said means for imparting conventional reciproca'ting lay motion to the lay.

15. A shuttle loom as defined in claim 14 in which said cam means includes a centrally mounted cam wheel having a cylindrical periphery and having an axiallyoutwardly extending power cam rise mounted at the periphery thereof, and in which said pick motion carriage comprises a guide portion designed to rideon the cylindrical periphery of said cam wheel to support said pick motion carriage in substantially horizontal position.

16. A shuttle loom as, defined inclaim 13 inwhich said guide portion comprises a vertically depending pormotion to the lay assembly; a pick motion carriage at either side of said loom mounted on the outside of the side frames thereof and reciprocable longitudinally of said loom; connecting rod means between said carriage and said means for imparting reciprocating motion to said lay assembly, for imparting a reciprocatingmotion to said carriages in accordance with the motion of said lay assembly; cam Wheels mounted on said drive shaft, said cam wheels each having an axially outwardly extending power cam rise at the periphery thereof at an angle of 180 the one to the other; power arms horizontally pivoted at one end on said carriages, and in operative connection at the other ends thereof with the picks of the loom; connector means operatively connecting one end of said power arms to said picker sticks at points intermediate the ends thereof; cam rollers mounted on the other ends of said power arms in position to contact with said cam rises as said cam wheels rotate to operate said picker sticks; and spring means connected to said power arms for returning picker sticks to their initial position after operation thereof.

18. A side pick motion assembly for shuttle looms comprising a pick motion carriage; mounting means for mounting said carriage on the side frame of aloom in longitudinally slidable relation thereto; connecting rod means connecting said carriage to a point on the lay assembly of the loom whereby the horizontal component of the lay motion is imparted to said carriage; a picker stick and picker stick actuating means mounted on said carriage; with the outer end of said picker stick in operative contact with a pick of the loom, said picker stick actuating means including a cam roller; a cam wheel mounted on a drive shaft designed to rotate once for every two travels forward of the lay and supported by the side frames of the loom; a power cam on the face of said cam wheel at the periphery thereof, said cam wheel being mounted in a position relative to said carriage whereby upon rotation of said cam wheel, said power cam will move into contact with said cam roller as the latter is carried rearwards on said carriage due to the motion imparted thereto by said connecting rod means to operate said picker stick actuating means and actuate the picker stick; and spring means in connection with said actuating means for returning the picker stick to its initial position after actuation thereof.

19. A side pick motion assembly for shuttle looms as defined in claim 17 in which said pick motion carriage is slidably mounted on a pump rod spindle supported by said supporting means, and is vertically swingable about said pump rod spindle, and in which said pick motion carriage comprises a guide portion designed to ride on the periphery of said cam wheel to support the pick motion carriage in substantially horizontal position.

20. A side pick motion assembly for shuttle looms as defined in claim 19 in which said guide portion comprises a vertical depending portion adapted to ride against the rear face of the cam wheel and designed to absorb axial thrust developed upon operation of said power cam.

References Cited in the file of this patent UNITED STATES PATENTS 

